Balanced head gimbal assembly for improved seeking performance

ABSTRACT

In a balanced head gimbal assembly for improved seeking performance, a slider having a magnetic head with a set of read elements to read data and a set of write elements to write data, an air-bearing surface, and a non-air-bearing surface is coupled to a suspension. The suspension includes a loadbeam, a flexure, and a balancing weight. The loadbeam is coupled to an actuator arm. The flexure, coupled to the loadbeam, has a window through which a dimple, coupled to the loadbeam, contacts a dimple contact point. The balancing weight, coupled to the flexure, has a configuration which permits alignment of a center of mass of the head gimbal assembly with the dimple contact point.

BACKGROUND INFORMATION

The present invention relates to a head gimbal assembly (HGA) for use ina magnetic information storage disk drive. In particular, the presentinvention relates to a HGA design having superior performance duringtrack accessing.

FIG. 1 illustrates a conventional hard disk drive design. Hard diskdrives are used as the major storage unit in a computer. Hard diskdrives operate by storing and retrieving digitized information onto andfrom a rotating disk. The reading and writing of the information ontothe disk is performed by a magnetic “head” embedded in a ceramic“slider” which is mounted on a piece of a metal spring, called asuspension. The suspension consists of many components, such as a loadbeam, a gimbal, traces, a hinge and a base plate. The suspensionprovides two functions: mechanical support and electrical connectionbetween the “head” and the “pre-amplifier.” The slider flies on therotating disk with about a 10 nm gap, also known as the flying height,between the slider and the disk. In order to make the slider fly stablyand reliably at such a small gap, various characteristics of thesuspension design must be carefully designed, such as vertical stiffness(Kz), gimbal pitch and roll stiffness (Kp, Kr), and gimbal staticattitude (pitch and roll static attitude (PSA and RSA respectively)).

The disk drive also typically includes a servo system that operates tomove a slider or a head over a defined track on a disk surface. Thisoperation is called a seeking operation. The performance or datatransfer rate of the disk drive is a key performance characteristic. Inorder to achieve a higher performance/data transfer rate, seeking hasbecome more aggressive, and is increasingly characterized by highspeeds, high acceleration, and high deceleration. During the seekprocess, the slider flying height may change due to: (1) changes ofairflow speed and direction; and (2) changes in suspension loads appliedon the slider during acceleration and deceleration. The changes insuspension loads applied on the slider during acceleration anddeceleration primarily occur due to the torque in the roll direction(for an in-line actuator). FIGS. 2 a and 2 b show examples of seekingacceleration and roll torque relative to seeking speed and as a functionof time. For these examples, during the acceleration process, a negativeroll torque is applied to the slider approximately at 0.5 ms. A positiveroll torque change occurs during the deceleration process approximatelyat 6 ms. These roll torque changes may reduce the clearance between theslider and the disk, and may cause the slider to contact the disk,resulting in a drive failure. Therefore, the change in roll torque needsto be improved.

Changes in the roll torque may equal the acceleration or decelerationmultiplied by the roll inertia moment. Conventionally, the roll torquemay be reduced by reducing the acceleration or deceleration, but doingso may result in a negative effect on drive performance. Therefore, itis preferable to reduce the roll inertia moment instead. Further, duringcertain seek operations, the servo may lose control of the actuator,resulting in a loss of control over the acceleration or deceleration ofthe slider. In these situations, the actuator may slam into crash stopsat the inner or outer diameters of the disk. During this process, theacceleration or deceleration of the slider may reach as high as tentimes the normal seek operation acceleration or deceleration. Moreover,as a result of the loss of actuator control, the slider may contact thedisk, resulting in severe damage to the disk and the slider. Onesolution for preventing damage to the disk was proposed in U.S. Pat. No.6,125,017, issued to Misso et al., in which the crash stop wasre-designed. Alteratively, another solution for preventing disk damageis to increase the breaking distance. This solution is not desirable asa larger braking distance directly reduces the disk area that can beused for data storage. Thus, it is even more preferable to reduce theroll inertia moment.

Thus, it would be desirable to have an improved head-gimbal assemblythat reduces the roll inertia moment of a slider.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 illustrates a conventional hard disk drive design.

FIG. 2 a illustrates a graphical example of seeking speed andacceleration as a function of time.

FIG. 2 b illustrates a graphical example of seeking speed and rolltorque exerted on a slider as a function of time.

FIG. 3 illustrates one embodiment of a conventional head gimbalassembly.

FIG. 4 illustrates one embodiment of a thin slider for reducing rolltorque.

FIG. 5 illustrates one embodiment of a head gimbal assembly for reducingroll torque.

FIG. 6 illustrates one embodiment of a head gimbal assembly for reducingroll torque.

FIG. 7 illustrates one embodiment of a head gimbal assembly for reducingroll torque.

FIG. 8 illustrates a graph showing the roll torque applied on variousslider embodiments as a function of time.

FIG. 9 illustrates a graph showing the roll torque applied on variousslider embodiments as a function of the thickness of a slider.

FIG. 10 a illustrates an embodiment of a conventional head gimbalassembly with a ramp limiter.

FIG. 10 b illustrates one embodiment of a balanced head gimbal assemblywithout a ramp limiter.

FIG. 11 a illustrates one embodiment of a balancing weight configurationfor a head gimbal assembly.

FIG. 11 b illustrates one embodiment of a balancing weight configurationfor a head gimbal assembly.

FIGS. 12 a and 12 b respectively illustrate a top and a side view of oneembodiment of a balancing weight configuration for a head gimbalassembly.

FIGS. 13 a and 13 b respectively illustrate a top and a side view of oneembodiment of a balancing weight configuration for a head gimbalassembly.

FIG. 14 illustrates in a flowchart one embodiment for reducing the rolltorque exerted on a slider during a seek operation.

DETAILED DESCRIPTION

A head gimbal assembly balanced to improve seeking performance isdisclosed. The head gimbal assembly may include a slider with a magnetichead having a set of read elements to read data and a set of writeelements to write data. The slider may have an air-bearing surface and anon-air-bearing surface. The head gimbal assembly also may have asuspension, including a loadbeam, a flexure, and a balancing weight. Theloadbeam may be coupled to an actuator arm. The flexure may be coupledto the loadbeam and the slider and may have a window through which adimple, coupled to the loadbeam, may contact a dimple contact point. Thebalancing weight may be coupled to the flexure and may have aconfiguration which permits the alignment of a center of mass of thehead gimbal assembly with the dimple contact point.

FIG. 3 illustrates one embodiment of a conventional head gimbalassembly. The head gimbal assembly (HGA) may include a slider 340 and asuspension to support the slider 340. The suspension may include aloadbeam 305 attached to an actuator arm (not shown). The actuator armmay position and move the HGA over various portions of a magnetic diskto read and/or write data to and from the disk. A flexure, including aflexure tongue 315, may be coupled or attached to the loadbeam 305. Theflexure may maintain relative in-plane alignment with the loadbeam 305while permitting the slider 340 to “pitch” and “roll” with respect tothe loadbeam 305. A flexible portion of the loadbeam 305 (not shown) maybe bent elastically to yield a gram load, or reaction force, which istransmitted to the slider through a dimple 310, causing the slider to bepressed downward toward the surface of the disk. The slider 340 may beattached or coupled to the flexure tongue 315 using epoxy 320 and/or apolymer 325, such as polyimide, both of which are known in the art. Theslider 340 also may be electrically connected to an electrical trace330, such as a copper trace, using a conductive material 335, such as asolder ball or a gold ball.

FIG. 4 illustrates one embodiment of a thin slider for reducing rolltorque. Conventionally, sliders have a thickness greater than 180micrometers. By reducing the thickness of a slider 440 to either 170micrometers or 140 micrometers, the thinner slider 440 may have asmaller inertia and a smaller distance (moment arm) between the centerof mass of the HGA and a dimple contact point, thus reducing the rolltorque exerted on the slider 440 during a seek operation. All otherelements in FIG. 4 are equivalent to corresponding elements in FIG. 3,similarly numbered except for the first digit. As shown in FIG. 8,reducing the thickness of the slider 440 may reduce the roll torqueexerted on the slider during seeking by various amounts depending on thethickness of the slider 440. Also, FIG. 9 illustrates scaled roll torqueexerted on a slider as a function of slider thickness. As the graphshows, by reducing the thickness of the slider 440 from 230 micrometers(as commonly found in the art) to 170 micrometers may reduce the rolltorque by approximately 40%.

FIG. 5 illustrates one embodiment of a head gimbal assembly for reducingroll torque. In this embodiment, roll torque exerted on a slider duringseeking may be reduced by creating a “window” or gap in the flexuretongue 515, thereby exposing a portion of the non-air-bearing surface ofthe slider 540. The window in the flexure tongue 515 may permit a dimple510 to bypass the thickness of the flexure tongue 515 and polymer layer525 and directly contact the non-air-bearing surface of the slider 540.Having the dimple 510 directly contact the non-air-bearing surface ofthe slider 540 may reduce the length of the roll moment armapproximately 30 micrometers for a conventional HGA design. Despite thereduction in the length for the roll moment arm, manufacturing andtesting a suspension having a flexure window as described in thisembodiment may be complicated, as the dimple 510 is unable to engage theflexure tongue 515 before the slider 540 is coupled to the flexure 515.This complication may prevent the control and measurement of the gimbalstatic attitudes and dimple contact force. Despite the manufacturing andtesting complications, a HGA having a flexure window may greatly reducethe roll torque exerted on the slider as compared to a conventional HGA,and as shown in FIGS. 8 and 9. All other elements in FIG. 5 areequivalent to corresponding elements in FIG. 4, similarly numberedexcept for the first digit.

FIG. 6 illustrates one embodiment of a head gimbal assembly for reducingroll torque. In this embodiment, roll torque exerted on a slider duringseeking may be reduced by creating a “window” or gap in the flexuretongue 615, which in one embodiment may be a stainless steel sheet,thereby exposing a portion of the polymer layer 625. A dimple 610 maycontact the exposed polymer layer 625. Advantageously, contacting thedimple 610 to the polymer layer 625 instead of the dimple 610 to thenon-air-bearing surface of the slider 640, as disclosed in theembodiment of FIG. 5, may reduce the length of the roll moment armapproximately 20 micrometers for a conventional HGA design and mayreduce the roll torque without the manufacturing and testingcomplications descried for the embodiment disclosed in FIG. 5.Additionally, contacting the dimple 610 to the polymer layer 625 mayreduce dimple Hertzian contact stress since the polymer 625 is lessstiff than the slider substrate. As a result, dimple wear may bereduced, and dimple topography may be better maintained throughout thelife of the disk drive. The location of the dimple contact also maydrift less than if the dimple contacted the surface of the flexuretongue. This embodiment also differs from and is advantageous over theHGA and method disclosed in U.S. Pat. No. 6,549,376 to Scura et al. inthat in this embodiment, the dimple height is reduced, and no additionalmaterial is added to the suspension. The polymer layer 625 provides, forexample, polyimide standoffs 620 and 625 between the flexure 615 and theslider 640.

FIG. 7 illustrates one embodiment of a head gimbal assembly for reducingroll torque. In this embodiment, a flexure 715 may have a window thatpermits a dimple 710 to contact the surface opposing the air-bearingsurface of the slider 740. Further, a substantially rigid balancingweight 745 may extend from a distal end of the flexure 715. Thesubstantial rigidity of the balancing weight 745 may prevent thebalancing weight 745 from resonating during operation of the disk drive,thus ensuring the slider flying height is not affected during operation.The balancing weight 745 may have a first component which is coupled toan extends vertically from the distal end of the flexure 715. In oneembodiment, the first component may extend perpendicularly from thedistal end of the flexure 715. Attached to the other end of the firstcomponent may be a second component having a horizontal orientation, inone embodiment, the second component may be parallel to the flexure 715.Together the two components of the balancing weight 745 may shift thecenter of mass of the slider 740 and gimbal closer to the point wherethe dimple 710 contacts the slider 740, thereby reducing the roll torqueexerted on the slider 740 during seeking. The reduction in roll torquefor this embodiment is demonstrated in FIGS. 8 and 9. All other elementsin FIG. 7 are equivalent to corresponding elements in FIG. 6, similarlynumbered except for the first digit.

FIG. 8 illustrates a graph showing the roll torque applied on variousslider embodiments as a function of time. As previously discussed above,the roll torque exerted on the slider during seeking operation lessensif one of the above embodiments are used in place of a conventional HGA.Further, using a combination of a thinner slider, a window in a flexureand a balancing weight in a HGA may produce the greatest reduction inroll torque.

FIG. 9 illustrates a graph showing the roll torque applied on variousslider embodiments as a function of the thickness of a slider. For aconventional HGA, decreasing the slider thickness may greatly reduce theroll torque exerted on the slider during seeking operation. If a HGAembodiment incorporates the window in a flexure feature, roll torque maybe reduced, and the reduction may be enhanced if used in conjunctionwith a thinner slider and/or a balancing weight. The graph also showsthat a HGA incorporating a thin slider of 140 micrometers, a window in aflexure, and a balancing weight may result in the greatest reduction inroll torque.

FIG. 10 a illustrates an embodiment of a conventional head gimbalassembly with a ramp limiter. The ramp limiter 1005 may be used inload/unload drives to protect a slider 1010 from damage if the disk isnot spinning. In these situations, a HGA may rest on a load/unload rampto prevent the slider 1010 from contacting the disk surface. The ramplimiter 1005 may also protect the slider 1010 in a shock event bycontacting a ramp support to limit the movement of the slider, therebypreventing damage to the slider 1010.

FIG. 10 b illustrates one embodiment of a balanced head-gimbal assemblywithout a ramp limiter. In this embodiment, the ramp limiter may beremoved and replaced with a balancing weight 1020. The balancing weight1020 may protect the slider during a shock event, with the upper portionof the balancing weight contacting the load beam during a shock event.As a result, the range of motion of the slider may be limited and damageto the slider may be prevented. Although the balance weight 1020 mayresemble a load/unload ramp limiter, it differs drastically fromconventional load/unload limiters in its mass. Unlike conventionallimiters, which are designed to achieve minimal mass, the balance weight1020 may be designed to have substantial mass for balancing purposes.The mass of the balance weight 1020 may depend on several factors,including the mass of the slider and the distance from the balanceweight to the tip of the dimple (not shown in this figure). One skilledin the art should realize that a balance weight 1020 with a larger massmay be required given a larger slider mass. The balance weight 1020 mayhave a smaller mass given a longer distance between the balance weightand the dimple contact point.

FIG. 11 a illustrates one embodiment of a balancing weight configurationfor a head gimbal assembly. In this embodiment, a HGA may have a flexure1115 coupled to a slider 1120. The slider 1120 may have a read/writehead 1125 located in a trailing edge of the slider body. The HGA alsomay have a balancing weight configured such that the center of mass ofthe HGA coincides with the point where a dimple (not shown) contacts anon-air-bearing surface of the slider through a window in the flexure(not shown), thereby reducing the roll torque exerted on the sliderduring seeking. The balancing weight may have a first component 1105located at a distal end of the flexure 1115. The first component 1105may rise vertically with respect to the flexure 1115 and may besubstantially rigid and have a substantial mass. The balancing weightalso may have a second component 1110 located at a proximal end of theflexure 1115. The second component 1110 also may rise vertically withrespect to the flexure 1115 and may be substantially rigid and have asubstantial mass. In one embodiment, one of or both of the first andsecond components 1105, 1110 may rise perpendicularly with respect tothe flexure 1115. As stated above, the mass of the balance weightcomponents may depend on the design of the HGA, with the dimensions andmass of the various HGA components affecting the mass of the balancingweight.

FIG. 11 b illustrates one embodiment of a balancing weight configurationfor a head-gimbal assembly. In this embodiment, a HGA may have a flexure1140 coupled to a slider 1145 which has a read/write head 1150 in itstrailing edge. A balancing weight may be configured to shift the centerof mass of the HGA to coincide with the contact point of the dimple andthe slider back side (not shown), thereby reducing the roll torqueexperienced by the slider during seeking. In this configuration, thebalancing weight may have a first component 1135 located at and coupledto a point between the proximal and distal ends of the flexure 1140. Thefirst component 1135 may rise vertically with respect to the flexure1140 and may be substantially rigid and have a substantial mass. In oneembodiment, the first component 1135 may rise perpendicularly withrespect to the flexure 1140. The balancing weight may have a secondcomponent 1130 coupled to the first component 1135 and orientedhorizontally. In one embodiment, the second component 1130 may beparallel to the flexure 1140. The second component also may besubstantially rigid and have a substantial mass.

FIGS. 12 a and 12 b respectively illustrate a side and top view of oneembodiment of a balancing weight configuration for a head gimbalassembly. In this embodiment, a HGA may have a flexure 1210 coupled to aslider 1215, which has a read/write head 1220 located in the trailingedge of the slider 1215. A balancing weight may be attached or coupledto the flexure 1210. The balancing weight may be configured in a “rail”shape running along the longitudinal axis of the flexure 1210. In oneembodiment, the balancing weight may be distributed among two or more“rails” 1205 running along the longitudinal axis of the flexure andsuspension. These rails 1205 may be placed on opposing edges of thesuspension or flexure and aligned in the direction of the longitudinalaxis of the flexure or suspension, the result of which may prevent thecreation of a moment in the direction perpendicular to the disk surface(i.e., the slider may not yaw during seeking) due to lateralacceleration. In one embodiment, the balancing weight components 1205may be placed on opposing sides of the suspension or flexure andoriented in the direction of the longitudinal axis of the flexure orsuspension, running at least the length of the slider, and therebyresulting in the stiffening the HGA and minimization of the dynamiceffect of the balancing weight. The distribution of the balancing weightmay align a center of mass of a substantially rigid portion of the HGA,including the balance weight and the slider, with the dimple contactpoint (not shown).

FIGS. 13 a and 13 b respectively illustrate a side and top view of oneembodiment of a balancing weight configuration for a head gimbalassembly. A HGA may have a flexure 1315 coupled to a slider 1320. Theslider 1320 may have a read/write head 1325 embedded or attached to thetrailing edge of the slider 1320. The flexure 1315 may have a window, orgap, through which a dimple (not shown), coupled to a loadbeam (notshown), may contact the slider back (i.e. the non-air-bearing surface ofthe slider). The HGA may also have a balancing weight coupled to theflexure 1315. In this embodiment, the balancing weight may have aconfiguration including a first components 1305 elevated from theflexure and oriented horizontally with respect to the flexure 1315. Inone embodiment, the first component 1305 may be parallel with respect tothe flexure 1315. The first component may be coupled or joined to theflexure through one or more support weight components 1310 which may belocated between and perpendicular to both the flexure 1315 and the firstcomponent 1305. The gaps or holes between the support components 1310may make the balance weight more efficient by raising the center of massof the balance weight. The holes or gaps also may reduce the airfloweffect on the HGA.

FIG. 14 illustrates in a flowchart one embodiment for reducing the rolltorque exerted on a slider during a seek operation. In block 1410, aslider thickness for a slider in a head gimbal assembly may be selected.Conventionally, sliders may have a thickness of approximately 230micrometers, but may be as thin as 140 micrometers. The thickness of theslider may affect the roll torque exerted on the slider during seeking,with thicker slider being subject to increased roll torque relative tothinner sliders. In decision block 1420, to reduce the roll torque aloneor in combination with the selected slider thickness, a window may becreated in a flexure in the head gimbal assembly. If the window iscreated, the window may expose a portion of a surface beneath theflexure. In one embodiment, the polymer layer sandwiched between theflexure and the slider may be exposed by the window. Alternatively, thewindow may be created in the flexure and underlying polymer layer,thereby exposing a non-air-bearing surface of the slider. If the windowis created, in block 1430, a dimple, coupled to the loadbeam, maycontact either the exposed portion of the polymer layer or thenon-air-bearing surface of the slider.

In decision block 1440, either alone or in combination with the selectedslider thickness and/or the window in the flexure, a balancing weightmay be configured such that when the balancing weight is coupled to theflexure, the center of mass of the HGA shifts and aligns with the pointat which the dimple contacts the exposed portion of the polymer layer orthe non-air-bearing surface of the slider. The balancing weight may besubstantially rigid and have a substantial mass. The balancing weightmay have multiple configurations, each of which may result in thealignment of the HGA center of mass with the dimple contact point. Inone embodiment, the balancing weight may have a first component coupledto and extending perpendicularly from a distal end of the flexure. Asecond component may be coupled to the first component and may beparallel or substantially parallel to the flexure. Alternatively, thebalancing weight may be distributed among two or more “rails” parallelto the longitudinal axis of the flexure and located on opposing edges ofthe flexure. In an embodiment, the rails may be elevated from theflexure with vertical supports joining the elevated rails to theflexure. The vertical supports may be spaced apart from each other,creating “holes” which may result in the shifting of the HGA center ofmass upward. The holes may also reduce the airflow effect on the HGA. Inanother embodiment, the balancing weight may have a first componentcoupled to and perpendicular with respect to the distal end of theflexure. A second component may be coupled to and perpendicular withrespect to the proximal end of the flexure. In another embodiment, thebalancing weight may have a first component coupled to and perpendicularwith respect to the flexure at a point located between the distal endand the proximal end of the flexure. Attached to the opposite end of thefirst component may be a second component. The second component may beparallel or substantially parallel to the flexure. In block 1450, ifused, the balancing weight configuration may be coupled to the flexureto align the HGA center of mass with the dimple contact point. If abalancing weight is not used, the process ends in block 1490.

In block 1460, if a flexure window is not created, the dimple maycontact the flexure. In one embodiment, the flexure may be made ofstainless steel. In decision block 1470, a balancing weight may or maynot be used. If the balancing weight is used, then in block 1480, thebalancing weight may be configured and coupled to the flexure. Thebalancing weight may have multiple configurations, each of which mayresult in the alignment of the HGA center of mass with the dimplecontact point. Exemplary embodiments of the various balancing weightconfigurations are described above. If the balancing weight is not usedto reduce roll torque, the process ends in block 1490. The result of theabove-described method for reducing roll torque exerted on a sliderduring seeking may use a thinner slider, a flexure window, and abalancing weight, in various combinations or individually, to reduceroll torque.

Embodiments of the invention described above may improve the seekingperformance of the HGA. While roll torque may be completely eliminatedwith a fully balanced HGA incorporating a thinner slider, a window in aflexure, and a balancing weight, those skilled in the art will recognizethat improved HGA performance may be obtained using any of theabove-mentioned and described features individually or combinations ofany two features. Further, those skilled in the art will recognize thatadditional balance weight configurations which align the center of massof the HGA with a dimple contact point may be employed to reduce rolltorque.

Therefore, the foregoing is illustrative only of the principles of theinvention. Further, those skilled in the art will recognize thatnumerous modifications and changes are possible, the disclosure of thejust-described embodiments does not limit the invention to the exactconstruction and operation shown, and accordingly, all suitablemodifications and equivalents fall with in the scope of the invention.

1. A head gimbal assembly, comprising: a slider with a magnetic headhaving a set of read elements to read data and a set of write elementsto write data, said slider having an air-bearing surface and anon-air-bearing surface opposing said air-bearing surface; and asuspension to support said slider and maintain a spacing between saidslider and a magnetic data storage medium, said suspension comprising: aloadbeam coupled to an actuator arm; a flexure coupled to said loadbeamand said slider, said flexure having an exposed portion through which adimple coupled to said loadbeam contacts a dimple contact point; aplurality of polyimide standoffs located between said flexure and saidslider, wherein said dimple contact point is located on a surface ofsaid plurality of polyimide standoffs; and a substantially rigidbalancing weight, coupled to said flexure, having a configuration topermit a center of mass of said head gimbal assembly to align with saiddimple contact point wherein said configuration comprises at least onecomponent coupled to said flexure and perpendicular to both alongitudinal axis of said flexure and the plane of said flexure.
 2. Thehead gimbal assembly of claim 1, wherein said balancing weight has afirst component perpendicular to both a longitudinal axis of saidflexure and said plane of said flexure and coupled to a point locatedbetween a distal end and a proximal end of said flexure and a secondcomponent coupled to said first component and parallel to saidlongitudinal axis of said flexure.
 3. The head gimbal assembly of claim1, wherein said dimple contact point is located on said non-air-bearingsurface of said slider.
 4. The head gimbal assembly of claim 1, whereinsaid slider has a thickness less than 180 micrometers.
 5. The headgimbal assembly of claim 1, wherein said balancing weight is coupled toand extends from a distal end of said flexure, said balancing weighthaving a first component coupled to and perpendicular to a longitudinalaxis of said flexure and a second component coupled to said firstcomponent and parallel to said longitudinal axis of said flexure, saidsecond component capable of contacting said loadbeam during a shockevent.
 6. The head gimbal assembly of claim 1, wherein said balancingweight is distributed among two components both parallel to alongitudinal axis of said flexure and located along opposinglongitudinal edges of said flexure.
 7. The head gimbal assembly of claim6, wherein said two components each have a portion parallel to andelevated from said longitudinal edge of said flexure and a plurality ofvertical supports coupled between and perpendicular to said portion andsaid flexure along said longitudinal axis of said flexure, wherein saidplurality of vertical supports are spaced apart a variable distance fromeach other.
 8. The head gimbal assembly of claim 1, wherein saidbalancing weight has a first component coupled to a distal end of saidflexure and perpendicular to both a longitudinal axis of said flexureand said plane of said flexure and a second component coupled to aproximal end of said flexure and perpendicular to both said longitudinalaxis of said flexure and said plane of said flexure.
 9. A disk drive,comprising: a slider with a read/write head having a set of readelements to read data and a set of write elements to write data, saidslider having an air-bearing surface and an non-air-baring surfaceopposite to said air-bearing surface; a magnetic data storage medium tostore data; a suspension to support the slider and maintain a spacingbetween said slider and said magnetic data storage medium, saidsuspension comprising: a loadbeam coupled to an actuator arm; a flexurecoupled to said loadbeam and said slider, said flexure having an exposedwindow through which a dimple coupled to said loadbeam contacts a dimplecontact point; a plurality of polyimide standoffs located between saidflexure and said slider, wherein said dimple contact point is located ona surface of said plurality of polyimide standoffs; and a substantiallyrigid balancing weight, coupled to said flexure, having a configurationto permit a center of mass of said head gimbal assembly to align withsaid dimple contact.
 10. The disk drive of claim 9, wherein said sliderhas a thickness less than 180 micrometers.
 11. The disk drive of claim9, wherein said balancing weight is coupled to and extends from a distalend of said flexure, said balancing weight having a first componentcoupled to and perpendicular to a longitudinal axis of said flexure anda second component coupled to said first component and parallel to saidlongitudinal axis of said flexure, said second component capable ofcontacting said loadbeam during a shock event.
 12. The disk drive ofclaim 9, wherein said balancing weight is distributed among twocomponents both parallel to a longitudinal axis of said flexure andlocated along opposing longitudinal edges of said flexure.
 13. The diskdrive of claim 12, wherein said two components each have a portionparallel to and elevated from said longitudinal edge of said flexure anda plurality of vertical supports coupled to and perpendicular to saidportion and said flexure along said longitudinal axis of said flexure,wherein said plurality of vertical supports are spaced apart a variabledistance from each other.
 14. The disk drive of claim 9, wherein saidbalancing weight has a first component coupled to a distal end of saidflexure and perpendicular to both a longitudinal axis of said flexureand said plane of said flexure and a second component coupled to aproximal end of said flexure and perpendicular to both said longitudinalaxis of said flexure and said plane of said flexure.
 15. The disk driveof claim 9, wherein said balancing weight has a first componentperpendicular to both a longitudinal axis of said flexure and said planeof said flexure and coupled to a point located between a distal end anda proximal end of said flexure and a second component coupled to saidfirst component and parallel to said longitudinal axis of said flexure.16. A head gimbal assembly, comprising: a slider with a magnetic headhaving a set of read elements to read data and a set of write elementsto write data, said slider having an air-bearing surface and anon-air-bearing surface opposing said air-bearing surface; and asuspension to support said slider and maintain a spacing between saidslider and a magnetic data storage medium, said suspension comprising: aloadbeam coupled to an actuator arm; a flexure coupled to said loadbeamand said slider, said flexure having an exposed portion through which adimple coupled to said loadbeam contacts a dimple contact point; and asubstantially rigid balancing weight, coupled to said flexure, having aconfiguration to permit a center of mass of said head gimbal assembly toalign with said dimple contact point wherein said configurationcomprises at least one component coupled to said flexure andperpendicular to both a longitudinal axis of said flexure and the planeof said flexure.
 17. The head gimbal assembly of claim 16, wherein saidsuspension further comprises a plurality of polyimide standoffs locatedbetween said flexure and said slider, and wherein said dimple contactpoint is located on a surface of said plurality of polyimide standoffs.18. The head gimbal assembly of claim 16, wherein said dimple contactpoint is located on said non-air-bearing surface of said slider.
 19. Thehead gimbal assembly of claim 16, wherein said balancing weight iscoupled to and extends from a distal end of said flexure, said balancingweight having a first component coupled to and perpendicular to bothsaid longitudinal axis of said flexure and said plane of said flexureand a second component coupled to said first component and parallel tosaid longitudinal axis of said flexure, said second component capable ofcontacting said loadbeam during a shock event.
 20. The head gimbalassembly of claim 16, wherein said balancing weight is distributed amongtwo components both parallel to a longitudinal axis of said flexure,located along opposing longitudinal edges of said flexure wherein saidtwo components extend perpendicularly from said longitudinal axis ofsaid flexure.
 21. The head gimbal assembly of claim 20, wherein said twocomponents each have a portion parallel to and elevated from saidlongitudinal edge of said flexure and a plurality of vertical supportscoupled between and perpendicular to said portion and said flexure alongsaid longitudinal axis of said flexure, wherein said plurality ofvertical supports are spaced apart a variable distance from each other.22. The head gimbal assembly of claim 16, wherein said balancing weighthas a first component coupled to a distal end of said flexure andperpendicular to both said longitudinal axis of said flexure and saidplane of said flexure and a second component coupled to a proximal endof said flexure and perpendicular to both said longitudinal axis of saidflexure and said plane of said flexure.
 23. The head gimbal assembly ofclaim 16, wherein said balancing weight has a first componentperpendicular to both said longitudinal axis of said flexure and saidplane of said flexure and coupled to a point located between a distalend and a proximal end of said flexure and a second component coupled tosaid first component and parallel to said longitudinal axis of saidflexure.